Actuator for speed changing mechanism



Nov. 3, 1953 l. H. wlLLlAMs E-rAx.

ACTUATOR FOR SPEED CHANGING MECHANISM 2 Sheets-Sheet l Original Filed Sept. 3, 1943 mms RMO/1 A. Saz/oer Nov. 3, 1953 1. H. WILLIAMS E'rAL 2,657,585

AcTuAToR FOR SPEED CHANGING MECHANISM Original Filed Sept. 3, 1943 2 Sheets-Sheet 2 Patented Nov. 3, 1953 ACTUATOR FOR SPEED CHANGING MECHANISM Ivor H. Williams, Birmingham, and Ralph K.

Super, Detroit, Mich., assgnors to The Timken- Detroit Axle Company, Detroit, Mich., a corporation of Ohio Original application September 3, 1943, Serial No. 501,172. Divided and this application February 21, 1946, Serial No. 649,308

This invention relates to actuators for speed changing mechanisms of the type disclosed in our pending application Serial No; 501,172, filed September 3, 1943, and of which the subject matter of the present application is a division.

The invention has more particular reference to a speed selecting actuator for multi-speed drive axles for motor vehicles in which means is provided for selectively driving the axle at high or low speed without declutching or disconnecting the train of drive mechanism from the source of power and the general object and purpose of the invention is to structurally simplify and increase the operating efficiency of actuators of this type.

In the operation of motor vehicles, particularly cf the heavy duty type, it is desirable to provide axle driveV gear ratios in addition tofthose afforded by the conventional variable speed transmission, which may be manually or automatically selectively controlled without declutching, and, while lthe selected transmission speed prevails, to increase or decrease the driving speed of the axle. Thus, instead of the usualthree or four transmission speeds, six or eight axle driving speeds 'are available to obtain maximum speed with economical fuel consumption in the operation of the vehicle under varying traffic and road conditions.

By the provision of the additional gear ratios, increased tractive effort at low speed is obtained, with greater fuel economy at high speed by reducing the engine speed necessary to maintain a predetermined road speed when the power required to maintain the road speed is not excessive. Since the two gear ratios at the axle double the range .of driving speeds. available by the conventional variable speed transmission, such twospeed axles have in recent years been generally adopted for use in heavy duty vehicles. In such vehicles it has been found preferable to employ a positive engagement of the toothed members in the speed ratio selector apparatus. Preferably, I use a speed changing mechanism of more or less recent development having a special tooth 14 claims. (o1. tft-364) construction in which a slidable toothed collar or Y and wherein these smooth Vendfaces intersectv the torque transmittingsurfaces of the teeth along sharp edges. The clearance or backlash between the coacting teeth is such'that when engaged end to end, said teeth will not intermesh in the relative rotation of the members butr will slidably abut at said end faces until a condition of substantial synohronism is established.

For the purpose of easily and smoothly shifting the collar which is usually rotated by the power drive out of mesh with one of the toothed members and into mesh with the other, by reason of the resistance due to high drive torque it is necessary to apply a force of relatively high magnitude to the collar to disengage the then engaged teeth, and then it is only necessary to apply to said collar a force of considerably less magnitude to engage the collar teeth with the teeth of the other member upon synchronization, so that an effective intermeshing relation of the teeth will be obtained without destructive clash or injury .to the parts.

The present invention generically comprehends a novel power operated speed ratio selector actuating unit wherein an energy storing device for accomplishing a final stage of shift operation in a speed ratio selector apparatus is built into the connection between a power element and a member adapted to be reciprocated thereby.

It is also an important object of the invention to provide simple and effective novel means for positively controlling and limiting the successive application of high and low magnitude Vpower operating forces to a shiftable toothed member in a drive speed changing mechanism.

A more particular object of the invention resides Ain the provision of a shiftable positive motion'transfer member having an energy storing device novelly housed therein and operatively connected between a shiftable toothed member and a power actuated element, whereby said device is preloaded and a high magnitude power force is applied to said shiftable member to disengage it from one toothed speed ratio selector member during the power stroke of said element, and thereafter said energy storing device alone acts to apply a lower magnitude power force to said shiftable member to urge said shiftable member toward mesh with another coacting toothed speed ratio selector member.

An additional object of the invention, in one embodiment thereof, is to provide a novel mounting and arrangement of the energy storing device and the energizing means therefor within an axially shiftable rail to which a clutch shifting fork is directly connected.

A further detailed object of the invention residesV in the provision of Y adjustable limit stops U for limiting shifting movement of a toothed member in response to the action of such an energy storing device.

With the above and other subordinate objects in View the invention comprises the improved power actuator and the construction and relative arrangement of its several parts, as will hereinafter be more fully described, illustrated in the accompanying drawings, and subsequently incorporated in the subjoined claims.

In the drawings wherein we have illustrated several concrete practical embodiments of our present improvements, and in which similar reference characters designate corresponding parts throughout the several views:

Figure l is a horizontal sectional View of a portion of a two speed drive axle housing illustrating one embodiment of our improved clutch collar actuator unit mounted upon the iront endl wall thereof;

Figure 2 is a fragmentary horizontal sectional view illustrating one mounting and arrangementv of the adjustable limit stops for the shifting fork;

Figure 3 is a sectional view similar to Figure l, showing a somewhat modied form of the invention using a diaphragm power element mounted on the side wall of the axle housing;

Figure 4 is a similar sectional view illustrating a further modification like that of Figure 3 but using a piston power element; and

Figure 5 is a detailed elevation partly in section of Ia portion of a modified power shifter device.

Referring for the present more particularly to Figure l of the drawings, indicates a part ofV a rear axle housing structure. In the illustrated embodiment a shaft driven through a pinion and ring gear set is journaled in housing i@ upon opposite end bearings I2 (only one illustrated) and is formed intermediate its ends with an enlarged portion having spaced sets of teeth IS and Iii. A shiftable clutch collar l is also provided with spaced sets of internal teeth It and il. Gears I3 and I0 of diierent size and constantly meshed with corresponding gears in the differential mechanism are journaled on shaft 1I and provided with sets of teeth 2| and 22 respectively.

In the illustrated position of Figure 1, collar I5 bridges tooth sets I0 and 22 whereby shaft and gear I9 are locked for rotation together. In the alternative position of collar I5 effected by the actuator to be described, the collar will bridge tooth sets I3 and 2| so as to lock shaft l! and gear I8 for rotation together. Collar I5 is always in toothed engagement with one or the other of gears i8 or le for driving the axle in a selected one of its available speeds.

A shifting fork 35i for clutch collar I5 is securely fixed in conventional manner to one end of a reciprocable shift rod or rail 36 which is axially slioably supported at its other end in an opening ed in one side wall of housing I 0- and in a stationary bracket or lug 38 laterally spaced from said side wall. Rod 36 and collar I5 slide in parallel paths.

The actuator device, generally indicated at 84, includes a base Se which is secured over an opening 85 in a housing boss 46 in the front end wall of housing it. Base 8B is secured to boss 46 as by cap screws 88. Base 86 is integrally formed with a hollow cylindrical boss 90 projecting through opening 85 into housing I0. A tubular rod S2 is .mounted for reciprocating movement in boss 90. Rod 92 is formed at its outer end with an internal bore or recess S3 which extends the greater part of its length and terminates in a shorter` reduced diameter bore 35 .closed by the reduced inner end of the rod at 91. Inner end 91 of rod 92 is operatively connected with one arm of a bell crank lever l-II pivotally mounted upon a rigid extension 9| of boss 90. The other arm of bell crank lever 'I4 is rockably engaged in a recess 'I5 provided in one side of the clutch fork shifting rod 55.

rlhe outer end of bore 63 is closed by a sealing ring V|05 and a disk |08 having threaded engagement in the end of rod @2. These closure members provide slide guide means for a coaxial piston rod Bil which is rigidly attached at its outer end to the center of a power driven piston element 96. Intermediate its ends, piston rod 9e is formed with a collar or annular enlargement 98 forming an abutment for the adjacent ends of coiled compression springs Ille and |62 respectively. The other end of the spring m0 has bearing contact against an internal annular shoulder me at the bottom of bore 93 while the other end of spring |02 is in bearing contact against the sealing member |05. Thus piston rod Q4 is connected to reciprocatory rod 92 by a resilient lost motion connection housed within rod 92.

Piston 96 Ihas reciprocatory movement within a cylinder |08 which is secured to base 86 by any suitable means, such as rivets H0, vand carries a packing seal ||2 surrounding rod 92. The outer end of the cylinder |08 is closed by a suitable cover ||4. Suitable conduits ||6 and IIB lead into the cylinder |08 from a suitable source of vacuum or other pressure at opposite sides of the piston 96. Stop members |20 and |22 respectively limit the travel of the piston 96 in each direction. These stop elements are of such length as to prevent possible distortion of the leather cup members at the periphery of the piston 95 and preserve the fluid sealing contact between the piston and the wall of the cylinder |08. These stops thus limit the axial movement of rod 92 and shift rod `36 in response to pressure diiferentials acting against piston S6, and additional means are provided for limiting further axial movement of rod 92 and shift rod 35 under the subsequent action of the energy storing springs |00 and |02 as will be explained.

Conduite ||6 and H8 are connected to a suitable selector valve such as that of Figure l2 of Brownyer Patent 2,398,407. As illustrated in Figure 1, this valve may comprise a housing |'I having a bore ||8 in which is slidable a cylindrical valve member I9 adapted to selectively connect a` vacuum line |2| either to conduit ||6 or conduit I|8 to apply differential pressures to opposite sides of the power element 96. supplies `atmospheric pressure to the conduit not connected to the vacuum, and a knob I 29 is provided for manual operation of the valve.

As shown in Figure 2, this additional means for limiting the axial movement of shift rod 36 comprises the two laterally spaced apart screws |24 and |26 respectively which are threaded in the wall of housing I0. with cone surfaced inner ends |25 adapted for engagement respectively by the chamfered or bevelled surfaces |21 on opposite sides of the hub of fork 34. Thus, by axially adjusting the screws |24 and |26 so as to vary the distance between cone surfaces |25, the overall limits of shifting movement of fork 34 maybe Vvariably adjusted.

These screws are provided' 5.. Each of the screws carries a suitable lock nut to fix the same in its adjusted position.

In the operation of the invention as above described, when pneumatic pressure is admitted through conduit ||8 to the cylinder |08 at the outer side of piston 96, or when vacuum is supplied through conduit I I6 to the other side of the piston 96, piston rod 94 is moved inwardly relative to reciprocable rod 92, thereby compressing spring |00.r After a limited relative movement between rods 94 and 92, spring |00 becomes solid and the entire fiuid pressure force acting on pistonV 96 is then transmitted without loss of power through said spring to rod 92 and applied through bell crank 'I4 to shifter rod 36 to slide clutch collar l5 to the left in Figure 1. Thus disengagement of the clutch teeth of collar I5 and gear 9 is accomplished by the initial power stroke of actuating device 84. Such disengagement does not take place until foot pressure on the accelerator is momentarily relieved, thus releasing the torque load on the engaged teeth. After such disengagement action is complete and, before clutch teeth I3 and 3| come into contact, further power driven movement of piston 96 is prevented by the limit stops |20. The energy stored in compressed spring is now available to continue the inward movement of rod 92, thus further shifting rod 36 and fork 34 in the same direction to contact teeth I3 of the clutch collar with teeth 2| of the other speed change gear I8. When teeth I3 and 2| contact they remain in sliding abutment by reason of the tooth formation above described and the pressure of spring |00 and when the speeds of rotation of said gear |8 and collar I5 are substantially synchronized, clutch I5 moves into smooth non-clashing intermeshing engagement with gear |8 under the pressure of spring |00.

When pneumatic pressure is admitted to cylinder |08 at the inner side of piston 96, or vacuum applied to the other side of piston 96, said piston is operated in the manner above described to shift rod 36 in the opposite direction to compress spring |02 and disengage clutch collar I5 and thereafter continue the movement of the clutch collar under the energy stored in spring |02 to establish an intermeshed relation between said collar and gear -|9.

Thus there is a two phase or two stage shifting movement of collar I5, the first or tooth disengaging movement of the clutch collar being effected by the power operated stroke of piston 90, while the second or intermeshing movement of the clutch collar is effected by the lesser power of the energy storing device housed within reciprocable rod 92.

In the form of the invention shown in Figure 3, the clutch actuating unit, instead of being mounted on the front wall of housing I0, is located at one side thereof and includes a diaphragm unit |4| enclosed in a casing member. In this case, a diaphragm rod 94 and energy storing springs Ille and |02 are directly mounted in a bore 93 formed in reciprocable clutch fork'shifter rod or rail |40 which carries shift fork 34 is supported for axial sliding movement on the housing sustantially in the manner above described. Bore 93 terminates in a smaller bore 95 into which the end of rod 94' projects, thus providing an internal shoulder |04' for lseating spring |06. Spring |021 reacts between enlarged formation 98 on rod 94 and the closure assembly |06' pro--l vided at the outer end of bore 93. Diaphragm rod 94 is thus slidably connected to reciprocable rod |40 and is also connected thereto by ,the

resiliently lost motion means housed within rod` The outer end of rod 94' is centrally secured to a power driven diaphragm element |44 which includes a flexible membrane |46 secured at its perimeter between marginal anges formed on the pneumatic pressure or vacuum receiving chamber sections |28 and |42 respectively.

Chamber sectionsv |28 and |42 comprise parts of casing member |4| and each casing part is provided with an outwardly extending flange. `rIhe flanges of the casing parts are secured together. Casing part |28 is secured, as by bolting, to the axle housing. The section 28 is secured to a. flanged cage 42 mounted in the side wall of the housing I0 and supporting the anti-friction bear- 'ing unit 44 for one end of shaft In this case also, limit stops |20 and |22 respectively are provided on chamber sections |20 and |42 to limit movement of the diaphragm |44 so that the power force Will be applied to that phase or stage of the shifting operation which involves only the dis' engagement of the clutch collar from the then en- `gaged gear element, while the meshing of the teeth on the collar with the clutch teeth on the other gear is accomplished in the subsequent second phase or stage by the energy stored in one or the other of the springs |00 or |02 as hereto- 'fore described in connection with the construction shown in Figure 1'. The pneumatic pressure medium or vacuum is supplied at opposite sides of the diaphragm |44 through the conduits 54 and 56 respectively. Conduits 54 and 56 are connected to the source of vacuum through a suitable manually operated selecting valve for controlling operation of the motor or diaphragm unit. This may be the selector valve illustrated at Figure l2 of Brownyer Patent 2,398,407 which is a continuation-in-part of Serial Number 387,977 filed April' 10i, 1941.v The same type of adjustable limit stops for the shifter rod and forli are provided as in Figure 1. In Figure 3, adjustable stops |34 and |36 for limiting overall travel of fork 34 are mounted in spaced stationary parts of the housing structure at opposite sides of the fork arm. The diaphragm unit at |4| thus provides power means for shifting the clutch shifter fork. This unit is a .double-acting double-ended vacuum operated motor because it is powered in either direction by selective application of vacuum through conduits 54 or 56.

Figures 4 and 5 illustrate further embodiments in which the mounting and arrangement of the energy storing springs directly within the hollow end of the fork shifter rail1 |40 is combined with the pneumatic piston and cylinder mechanism of Figure 1, instead of the iiuid pressure operated diaphragm of Figure 3. In Figure 5, the piston and cylinder construction is substantially identical with that shown in Figure l, while in Figure 4 the parts -are in reversed position and the :cylinder cover member is mounted in xed relation to the axle housing I0 while theI body wall of the cylinder is peripherally flanged and detachably secured to the cover member. As will be readily understood,.the shifter of Figures 4 and 5 operates to provide a two stage shifting motion of the ciutch fork, in the same manner as the construction shown in Figures 1 and 3.

From the foregoing, the construction and manner of operation of the several sclected'embodiments of the invention will be readily understood. It will be seen that by embodying an energy storingdevice in the two stage operating con- 7 nections between theclutch shifter forkand the power actuated element, which energy storing means preferably comprises a spring means housed within a reciprocable rod and functioning in each direction of movement thereof, we have materially simplified and increased the operating efliciency of prior actuator devices of this type. Also the simple and compact arrangement herein disclosed results in a more accurately controlled two stage shifting movement of the clutch collar and a final smooth and noiseless intermeshed engagement of the teeth thereon with the clutch teeth on the driving gear. The simple and rugged structural form of several cooperating elements has resulted in economical production with high operating efflciency.

While our present improvements are of general application to all classes of motor vehicles, the invention is particularly advantageous in the operation of heavy duty vehicles such as large capacity trucks where reduction in running time, low operating costs and increased earnings per ton mile are factors of prime consideration. With the conventional single speed axle it is necessary to compromise between'pulling ability on grades and top speed on level roads. Such a compromise is unnecessary in the use of a two speed double reduction axle which enables the operator to obtain both pulling ability and speed, or in other words, the best gear ratios for both extremesof operating conditions. Such a two speed axle with our improved clutch actuating unit enables the operator to pre-select at will the high or low axle gear ratios, the clutch shift being carried out with maximum speed and facility, under normal operating conditions and without declutching and consequent loss of headway. Thus, both maximum pulling ability and speed with prevalent heavy loads can be obtained under varying road conditions, resulting in lower fuel consumption and maximum economy of operation.

The invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein.

What is claimed and desired to be secured by United States Letters Patent is:

l. In actuating means for a shiftable gear ratio selecting member, a supporting member, a reciprocable fork shifting rail mounted on said supporting member, a reversibly operable power actuated member, means limiting travel of said power actuated member to a predetermined disstance in either direction, and connecting means between said power actuated member and rail to transmit controlled forces of different magnitudes in immediate sequence'to said rail, including means carried by the rail rendered effective during movement of said power actuated member in either direction and operable after conclusion of said movement of said power actuated member to apply a flnal reduced force to continue movement of the rail in said direction, said last-named means comprising spring means housed within a tubular portion of the fork shifting rail.

2.111 a speed changing mechanism wherein va rst toothed .member is shifted-out of engagement with a second toothed member and into engagement with a third toothed member, a power driven element and means interconnecting said element and said first toothed member comprising a reciprocable member .and a resilient lost motion connection housed Within said vreciprocahle member, and stop means for limiting the length of stroke of said power driven element sothat application of direct power drive from said element to said rst toothed member is veffective during disengagement of said rst andsecond toothed members but is interrupted prior to engagement of said second and third toothed members, said resilient connection being compressed during the stroke of said .power Vdriven'element and expanding to continue shift `of said "rst toothed member in the same 'direction into f engagement with said third toothed member'fwhen their speedsare synchronized.

3. In an automotive vehicle'provi-ded` with 'a multi-speed axle including a casing member and reciprocable shift fork; .means for operating said multi-speed axle to vestablish thesame in either a high gear setting orr 'a low igear setting, power means for moving said multi-speed 'axle operating means in `one or the other of two directions to effect the aforementioned operatifm of 'the axle mechanism, saidY power means coinprisingfa double-acting double-ended vacuum z operated motor comprising two casing parts'each part provided with an `outwardly extending flange, said flanges being secured together, said motor further comprising a reciprocable power element, force transmitting means interconnecting said power element with the aforementioned reciprocable shift fork, said force transmitting means including a hollow rod secured to the shift fork, a rod secured to the power element and housed within said hollow rod and means includingyieldable means interposed between and constituting the connection between said rods, said power means further includin-g afselector valve for controlling the operation of'said motor.

4. In actuating ymeans Ifor a shiftable gear ratio selecting member, a vacuum motor comprising a motor casing adapted to be secured toan axle housing, a power element movably mounted withing said motor casing, a shifter rod having a hollow end portion, a secondrod ysecured to said power element and projecting through said motor casing into the hollow portion of said shifter rod, and spring means housed by said hollow rod portion and surounding said second rod for yieldably interconnecting said rods,-said spring means being compressed during initial movement of said power element in either direction and subsequently expanding to accomplish a gear'shifting movement of said shifter rod.

5. In the actuating means dened in claim Il, said motor casing comprising two parts secured together along adjacent peripheries, and stop means on each casing part adapted to be engaged by said power element for limiting travel of said power element in both directions within said casing.

S. In a speed ratio selector mechanism, a toothed member movable intoand out of `engagement with either of two. other relatively rotatable toothed members, said members which 'are engaged being normally maintained against relative axial movement and released for relative axial movement uponinterruption of torque therebetween, energizable power means operably connected to saidmovable toothed member, a

connection between said power means and said movable toothed member comprising two relatively slidable members yieldably connected by spring means housed by one of the slidable members, said power means when energized being operable upon release of said torque for disengaging said movable toothed member from that one of said other toothed members which is engaged therewith and moving said movable toothed member toward but short of engagement with the other of said two toothed members with relatively high power, said spring means being energized during said high power actuated movement of said movable toothed member, and means comprising said energized spring means immediately eiTective upon said movable toothed member after completion of its high power travel for moving said movable toothed member into engagement with the other of said two toothed members with materially reduced power.

7. In a speed change mechanism for moving a rst toothed member out of engagement with a second relatively rotatable toothed member and into engagement with a third relatively rotatable toothed member, a fluid motor ycomprising a casing containing an element movable in response to fluid pressure differentials on opposite sides, a power driven member rigid with said element and projecting from the casing, a speed change control member mounted for reciprocation, means providing a relatively slidable connection between said power driven and control members, compressible spring means enclosed within said connection between said members, means for limiting the stroke of said power driven member in either direction, said first and second toothed members being disengaged and said spring means being compressed during the stroke of said power driven member in one direction, and means for limiting said stroke to stop high powered actuation of said rst toothed member before it engages said third toothed member while permitting said compressed spring means to expand to engage said rst and third toothed members when they are synchronized.

8. In actuating means for a shiftable gear ratio selecting mechanism, a uid motor having a movably mounted power driven element, a shifter member having a hollow end portion, a second member secured to said power driven element and projecting into the hollow portion of said shifter member, and spring means housed by said hollow portion and surrounding said second member for yieldably interconnecting said members, said spring means being compressed and said shifter member being moved a predetermined distance to accomplish a gear shift operation during movement of said power driven element in either direction, and said compressed spring means subsequently expanding to accomplish a further gear shifting movement of said shifter member.

9. In a change speed mechanism, a housing containing variable speed gearing and a gear shifter fork and having an opening, a reciprocable rail within the housing secured at one end to said fork and having a hollow bore at its other end, a motor casing secured over said opening in the housing, a power driven reciprocable shaft projecting from said motor casing into said bore, said shaft being slidably guided within said rail, rand cooperating spring and stop means within said bore interconnecting said shaft and rail in both directions of movement of said shaft.

10. In the change speed mechanism defined in 10 claim 9, stops projecting into said housing for engagement with said shifter fork for limiting its movement in either direction.

11. In combination with a housing containing variable speed mechanism and having an opening, a speed ratio selector within said housing, actuating means for said selector comprising a iiuid motor secured to said housing and having a casing, a base on said casing having a boss projecting into said housing through said opening,

a bore in said boss, a power element reciprocable within said casing, a first member slidably supported in said bore and projecting into the casing, and a member rigid with the power element and slidably connected to said rst member, and spring means enclosed in the connection between said members adapted to be compressed upon relative sliding movement of said members in either direction.

12. In the actuating means dened in claim 11, a projection on said boss, a bell crank pivoted on said boss with one end in pivotal connection with said rst member and an operable connection between the other end of said bell crank and said speed ratio selector.

13. In actuating means for a speed ratio selector mechanism, a uid motor casing having an opening in Aone end wall, a gear shifter member extending slidably through said opening into said casing and having an outer end externally of said casing and a bore in its inner end opening into the casing, a power element within the casing shiftable upon application of fluid pressure differentials to opposite sides thereof, a rod rigid with said element extending within the bore, spring means surrounding said rod within the bore, and cooperating parts on said spring means and rod and within said bore operable for yieldably connecting the rod and gear shifter member when said power element is shifted in either direction.

14. In an automotive vehicle provided with an internal combustion engine having an accelerator for in part controlling the operation of said engine and a two speed rear axle gear mechanism including rotatable members to be meshed and demeshed, a reciprocable shifter rod, power means for moving said rod comprising a motor and a stem operated thereby to move said rod in one or the other of two directions to establish or disengage the axle mechanism in either one or the other of its two settings, said rod having a spring mechanism enclosed therein, said motor when energized serving to operate said spring mechanism to move said rod to move the two speed gear mechanism toward one of its two gear ratio settings and to compress said spring mechanism, said spring mechanism when expanding serving to further move the axle mechanism in the same direction to establish or disengage the mechanism in one of its two settings as said members of said gear mechanism are synchronized.

IVOR H. WILLIAMS.

RALPH K. SUPER.

References Cited in thev file of this patent UNITED STATES PATENTS Number Name Date 1,720,989 Ahlm July 16, 1929 1,740,818 Killingsworth Dec. 24, 1929 1,955,751 Rush July 10, 1934 2,356,598 Lang et al Aug. 22, 1944 2,373,259 Price Apr. 10, 1945 

